Drilling and tapping machine



Sept. 21, 1937. J. F. BUHR DRILLING AND TAPPING MACHINE Filed Jan. 2, 1935 6 Sheets-Sheet l IIIIII'IIIII'II I4 Jos ep/v F 50/?! J. F. BUHR 2,093,546

DRILLING AND TAPPING MACHINE Filed Jan. 2, 1935 6 Sheets-Sheet 2 IIIIIII- WW -W u LII Se t. 21, 1937.

Sept. 21, 1937. J. F; BUHR I DRILLING AND TAPPING MACHINE Filed Jan. 2, 1955 e Sheets-Sheet s gwue/wfo'o v JoSe h F. 50hr Sept. 21, 1937. J. F. BUHR 2,093,546

DRILLING AND TAPPING MACHINE Filed Jan. 2, 1935 6 Sheets-Sheet 4 Sept. 21, 19 7. J, B HR 2,093,546

DRILLING KND TAPPING MACHINE Filed Jan. 2, 1935 6 Sheets-Sheet 5 Fly. /4

awe/whom J. F. BUHR DRILLING AND TAPPING MACHINE Sept. 21, 1937.

Filed Jan. 2, 1955 6 Sheets-Sheet 6 ZZZ ZZZ

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Patented Se t. 21, 1937 await tries h 17 Claims. This invention relates todrillin'g and tapping machines and more particularly to such machines provided with mechanismffor automatically providing slow feeding speeds and rapid traversing speeds. 1

'In the machine according to this invention the traversing and feeding fmovement of the tool is produced by a cami Heretofore in cam operated machines arranged for slow feedingand rapid traversing, the feeding and traversing speeds and the distances through which each operate have been produced wholly by the design of the cam.

J.Thus for each combination of feeding and traversing and of relative distances through which each operate, a different cam has been required. The result thus was the requirement of a large supply of cams. Furthermore, when new pieces of work had to beoperated on, it often happened that a new cam had to be made to retain the desired relation between feeding and traversing speeds and distances. As an example let it be supposed that in the case of the prior practice the .machine was fitted with a cam for feeding at B feeding speed through X distance and Ctraversing speed through Y distance. Also the next job tobe performed required feeding at B speed through X distance and C traversing speed through Y distance. It is obvious that a new cam would be required. Corresponding cam changes also had to be made for changing from drilling to tapping, requiring a further set of cams. Clearly a complete setof cams wouldbe infinite. in number.

According to the present invention all of the above objections are eliminated by providing a cam which drives its follower at a constant speed and providing independent feeding and traversing drives, the rates of which may be independently adjusted. In addition the length of the feeding and traversing is adjustable through an adjustable dog" mechanism. This construction permits great flexibility in both drilling andtapping and on anypiece of work. In drilling blind drilling and tapping machine in which the axial movement of the toolis provided by a cam and the rate of axial movement is controlled by an automatically operated dog controlled clutch.

Another object of this invention is to provide a drilling and tapping machine where the traversing speed is superimposed over the feeding speed through the'medium of an overrunning clutch. g

A further object is to provide a novel starting and stopping mechanism.

Further objects reside in the combination and operation of theparts to produce a positive and efficient mechanism. p

These and'other objects will be apparent from the following specification when taken with the accompanying drawings in which,

Fig.1 is a partial vertical section taken through the longitudinal central axis of the machine. showing a part of the feed mechanism which is located in front of the section,

. Fig. 2 is an elevation of the right end of the machine as viewed in Fig. 1 having at its center portion the coveri'ng plate and end supporting.

frame broken away,

Fig. 3 is a section on line III--III of Fig.2 showing the main clutch,

Fig. 4 is a section on the line IVIV of Fig. 2 showing the traversing control clutch,

Fig. 5 is a section onthe line V--V of Fig. 1 showing the overrunning clutch connection between the feeding and traversing v mechanism,

Fig. 6 is a cross-section of the overrunning clutch taken on line VI-VI of Fig. 5,

Fig. 7 is a view of a portion of the left side of the machine as viewed in Fig. 2 with the covering plate removed showing the feeding change gear mechanism, i Fig. 8 is a section'on line VIII-VIII of Fig. 2 showing the stopping mechanism and the dog and clutch mechanism controlling the feeding and traversing,

Fig. 9 is a developed portion of the dog drum of Fig. 8showing thetraversing initiating and stopping dogs in position, i

Fig. 10 is a section on line X-X of Fig. 9 showing the structure of a dog and the manner in which it is secured to its drum,

Fig. 11 is a fragmentary section taken on line XIXI of Fig. 8 showing a detail of the traversing stopping mechanism,

Fig. 12 is a section on the line -XII-.-XII of Fig, 8 showing a detail of the traversing initiating mechanism,

' i Fig. 13 is a fragmentary view showing a detail of the machine stopping and starting control device,

Fig. 14 is a fragmentary view of the right side of the machine as viewed in Fig. 2 showing the traversing change speed gears with their covering plate removed and an elevation'of the starting and stopping control device,

Fig. 15 is a View taken on the line XVXV of Fig. 1 showing the front end of the machine and being broken away to show the details of the starting and stopping control devices,

Fig. 16 is a view of a portion of the starting and stopping control device having the left portion as viewed in Fig. 15 broken away in part to show details of construction,

Fig. 17 is a fragmentary view showing the spindle traversing and feeding, operating head and the follower against which the main driving cam operates to axially move the spindle,

Fig. 18 is a fragmentary side view broken away in part showing details of the follower engaged by the main driving cam,

Fig. 19 is an elevation of the main operating cam for providing a constant speed stroke and return to the follower, and

Fig. 20 is a plan view of the main operating cam as shown in Fig. 19.

Referring to Fig. 1 of the drawings the machine is enclosed in a housing I. The housing i is divided into two sections by a central partition 2 and is closed at the front and rear by cover plates 3 and 4, respectively. At the rear of the housing I and within the cover plate 4 is a supporting frame 5 in which there are mounted various shafts and pins of the machine.

Power is supplied to the machine through the main driving shaft 6 which in turn is driven by the pulley l' keyed or otherwise suitably retained thereto. The rear end of the shaft 6 is mounted in a bearing 8 supported by the frame 5 and the front end of the shaft 6 is mounted in a bearing 9 supported in the bracket l0 comprising a portion of the housing I.

The tool being driven is rotated by the spindle I l and is preferably axially moved, together with the spindle H, by the unidirectional stroke and returns endless double-end screw cam i2 continuously rotatable in one direction throughout a complete cycle of operation, having portions for providing the follower with a constant speed stroke and return. It will be observed in Figs. 19 and 20 that the cam It comprises two opposed helical portions lZa and 52b. Obviously, types of cams other than the double-end type may be used. Further, cams having a constant pitch over only a portion of their operative surfaces may find application within the scope of the present invention. Such a case might be where the usual traversing and feeding is done over the constant pitch stroke portion of the cam and a special axial movement of the spindle is provided by the remaining portions of the cam. The main driving shaft 6 is hollow and receives the spindle H to which it is splined by means of keys l3 and the axially extending slots M.

The feeding and traversing speeds of the driven tool are determined by the speed of rotation of the cam i2. That is, for slow feeding speeds the cam l2 rotates slowly and for quick traversing speeds the cam i2 rotates relatively quickly. Power for driving the cam ill at both feeding and traversing speeds is taken from the main driving shaft 6 through the gear E5. The gear l5 may be either formed integrally with the shaft 6, as shown, or may be secured thereto in some suitable manner as by shrinking. The gear I5 drives the gear l6 mounted on the shaft l7.

Mounted on the shaft 11 is also a gear 58 which drives a gear l9 connected to any suitable oil pump for supplying pressure lubrication to the mechanism in a manner conforming to standard practice but not shown. See also Fig. 2.

The main operating clutch including part of the mechanism for driving the cam l2 at feeding speeds is shown in Fig. 3. The gear it, as shown in Figs. 1 and 2, drives the gear 25 shown in Fig. 3. The gear 25 is freely mounted on the shaft 26 being supported by antifriction bearings El, and is provided with an elongated sleeve 28 having at one end thereof a toothed clutch face 25!. Splined to the enlarged portion 39 of the shaft 26 for axial movement thereon is a yoke block 3! having a toothed clutch face 32 engageable with the clutch face 28. Fitting over the yoke block 3! is a yoke 33 fixed to the longitudinally slidable shaft 3d. The shaft 35 is mounted in the bracket 35 comprising a portion of the central partition 2 and the sleeve 3% extending from the form 5. Within the sleeve 36 is disposed a helical spring 3? maintained under compression and abutted at one end against the shaft 351 and at the other end against the cover plate 4. Normally the action of the spring 3'! forces the yoke 33 to the left and the clutch including the faces 32 and 29 is disengaged. Upon the moving of the shaft 3-; to the right in a manner later to be described the clutching faces 32 and 29 are engaged, with the result that the rotating gear 25, through the clutch faces 32 and rotates the yoke block 3 i. The yoke block 3! being splined to the enlarged portion 3i? of the shaft 28, rotates shaft 26, which rotates the gear G8 keyed to it. The gear it meshes with the gear see l, to drive the shaft 12 and the worm d3 mounted thereon. The worm 3 is in mesh with and drives a worm gear 44 mounted on a shaft 45. The shaft 45 has mounted thereon a gear 56. See Fig. '7. The gear 46 is located in a change speed gear box M and is in mesh with a gear l8 mounted in the slot 49 of the fixed bracket 50. A nut 5! is arranged to take up on the headed bolt 52 to maintain the gear 48 in adjusted position in the slot 5.9. It is to be understood, however, that any suitable change speed gear mechanism may be used.

The gear 48 drives a gear 53 secured to the shaft 5%. The shaft 54 is secured to and drives the outer cylinder 55 of the overrunning clutch 59. The overrunning clutch comprises, in addition to the outer cylinder 55, an inner cylinder 68 keyed or otherwise suitably secured to the shaft iii. In the surface of the inner cylinder 69 are cut one or more triangularly shaped notches with one side extending substantially radially, each having disposed therein a cylindrical bar 63 of slightly less diameter than the depth of the notch measured at the radially extending side. Thus upon rotating the outer cylinder 55 in a clockwise direction, the cylindrical bar 53 will be wedged between the inner cylinder and the outer cylinder 55, whereby when the outer cylinder 55 is rotated in a clockwise direction the inner cylinder Bil will be rotated therewith together with the shaft iii.

The shaft Si is supported for rotation in suitable bearings (55, t5 and 6'? and has secured thereto a worm 68. The worm 68 engages with and drives a worm gear (it. The worm gear is keyed to and drives the rotatably mounted sleeve 'iil having integrally formed thereon, or otherwise secured thereto, the cam It by means of which the tool supporting and driving spindle i l is axially moved.

The mechanism just described for rotating the cam I2 is for axially moving the spindle II at feeding speed. The cam I2is rotated at a rapid traversing speed by means of mechanism driving thus is thrown into and out of operation by the engagement and disengagement of the main clutch faces 82 and 29. The gear 40 is in mesh with and drives the gear I5 shown particularly in Fig.4. The gear I5 is mounted for rotation upon the short shaft 'lfisupported by the frame 5 and the bracket IT extending from the main housing I. The'gear I5 drives the gear 18 mounted for free rotation on the shaft 19 which is supported by the bearings 88 and 8i. The bearings 85 and 8! are mounted, respectively, in the frame 5 and the bracket 82 extending from the main housing I. The gear l8 is provided with an elongated sleeve 83 havinga toothed clutch face 84. The clutch face 84 is adjacent to and adapted for v engagement by the toothed clutch face 85 on the frame 5 and at the other end in the bracket 99,

see Fig. 8, extending fromthe main housing I.

As viewed in Fig. 4 theleft end of the axially moving rod 89 extends intoa bore 9| and has threaded thereint'o the flanged cap screw 92. Mounted on the portion of the rod 89 within the boreQI' and bearing against the flange of the cap screw 92 and one end of the bore BI is a helical spring 95 for normally urging the rod 89 to the left to move the yoke block 88 to engage the clutch faces 84 and 85. The axial movement of the rod 89 is controlled by the dog and latch mechanism shown particularly in Figs. 8 through Upon engagement of the clutch faces 84 and 85 the freely rotating gear I8 rotates the yoke block 88 which, being splined to the enlarged portion 87 of the shaft I9, drives the spiral gear 96 keyed to the shaft 19. The spiral gear 98 meshes with and drives a spiral gear 91 and through it the shaft 98 to which it is keyed. The shaft 98 extends laterally of the machine and intothe traversing change speed gear box 12 where it has mounted thereon the gear 99. See Figs. 2 and 14. The gear 99 meshes with a gear I89 mounted on the bracket IilI pivoted about the shaft 98. The bracket IIH is provided with a slot I92 through which extends a bolt I89 passing through a bracket I94. A nut I95 is threaded to the bolt I03 and is arranged to clamp the bracket I8I in adjusted position in a manner well known in the art. The gear I99 meshes with and drives the gear II secured on the shaft 6|. Theshaft 5| is shown particularly in Fig. 5 and, as above described, has secured thereto the worm 68 and the inner cylinder 58 of the overrunning clutch 59. By changing the adjustment of the bracket I98 I and the size of the gear in the change speed gear .box I2 on the shaft 6| the speed of rotation of the shaft BI may be varied in a well known manner. The. shaft 6| is extended from the change speed gear box 12 and has a squared end III] for receiving a crank for manual traversing.

Referring to Figs. 8 through 12 wherein is particularly shown the dog and latch mechanism for operating the traversing controlling clutch shown in Fig. 4:, the rotatably mounted sleeve I0 carrying the feeding and traversing cam I2 shown in Fig. 1, is extended to the rear of the worm gear 69 thereon, where it has mounted a drum III having two annular dovetailed grooves H2 and H3 in its surface. The drum III abuts at one end against the sleeve 10 supporting bearings I I4 and is clamped. thereagainst by the bushing H5 threaded into the end of the sleeve I8. Disposed in the annular dovetailed grooves H2 and H3 are camming dogs H8 and H9, the former being arranged for camming its follower radially of the drum and the latter being arranged for camming its follower axially of the drum. The dogs H8 and H9 are, aside from their camming surfaces, of the same construction. Each is made of two halves having flared portions extending under the edges of their respective annular dovetailed grooves. Each of the dogs is tapped to receive set screws I29 at each end, each tap having onehalf disposed in opposed sections of the longitudinally split dogs. The dogs are made in two halves so that each may be inserted in its respective groove. They are secured in position by the set screws I28 bearing against the bottom of the grooves. The dogs are thus forced upwardly, their lower flared portions engaging with the sides of the grooves and binding them in position.

Briefly stated, the traversing clutch shown in Fig. 4 is operated in the following manner: The clutch operating rod 89 is axially moved to the left, as viewed in Fig. 8, against theaction of the helical spring 95 by the dog I I9 and is moved to the right when the dog IE8 cams its follower i2I upwardly to release the detent I22 permitting the spring 95 to move the rod 89 to the right or rearwardly.

As shown in Figs. dand 8 the dog H9 has just engaged with its follower wheel I25 rotatably mounted on the inner end of the rod 89, thus drawing the rod 89 to the left against the action of the spring 95 opening the clutch faces 84 and 85 to stop the rapid traversing. At the same time the detent I22 mounted on the slidable block I26 resiliently pressed downwardly by the helical spring I21, is forced into the notch I28 in the rod 89 to lock the rod 89 in its left or clutch open position, after the dog H9 has moved from its position engaging its follower wheel I25. The drum III then continues to rotate until the dog H8 engages the follower wheel I29 on the follower i2l to lift the block I26. On the lifting of the block I26, the detent I22 secured thereto is lifted from the notch I28 thereby allowing the spring 95to move the shaft 89 to the right, as shown in Fig. 8, to engage the clutch faces 84 and 85 (Fig. 4). As heretofore explained, the engaging of the clutch faces 86 and 85 results in the driving of the cam I2 at traversing speed. After the dog I I8 has passed the follower wheel I29 and a predetermined traverse has been given to the spindle II, depending on the relative positions of the dogs H8 and H9, the dog H9 comes into engagement with its follower pins I66 and I61.

ersing of the tool may be obtained. The starting and stopping mechanism, which operates the main clutch, is shown particularly in Figs. 13, 14, i5 and 16. The shaft 34 carrying the yoke 33 which engages and disengages the main clutch having faces 32 and 29, see Fig. 3, is axially moved by an eccentrically disposed pin I35 supported by the rotatable shaft I36, bearing against the fork I 37. The shaft IE6 is supported by the main housing I and the pillow block I38 and is maintained against axial movement by the nut ISQ and the shoulder I66. Oscillating movement is supplied to the shaft I36 by the compressed air operated piston MI. The piston MI is disposed in a cylinder I62 and has therein helical springs I63 and III- l for urging the piston to substantially center position. The cylinder is connected to any suitable source of compressed air by a pipe I46 and controlled by button operated valves I46 and Ml. The operation is such that when the button operated valve I 46 is pressed, compressed air is conducted through the pipe I43 to the upper portion of the cylinder M2 to drive the piston downwardly. Release of force directed against the button operated valve M6 cuts off the supply of compressed air and permits the piston MI to be returned to its normal position. Pressure on the button operated valve Mil admits air to the lower portion of the cylinder I42 through the pipe M9 to drive the piston I lI upwardly. Release of force directed against the button operated valve Hill cuts off the supply of air to the lower portion of the cylinder I42 and permits the piston MI to be returned downwardly to its normal position. The piston I II acts through a piston rod I55 on the arm I56 to give it a partial rotation in either direction depending on the movement of the piston I II. The connection between the arms I56 and the piston rod I55 is provided by the adjustably threaded spaced nuts I5'I and I58 on the piston rod I55 and the fork having disk shaped arms I56 on the end of the arm 56. The disk shaped arms I59 straddle the piston rod I55 between the nuts I51 and I58 in such a manner that the movement of the piston rod I55 is imparted to the arm I56.

The arm I56 is integrally formed with or suitably secured to the casing I60 comprising approximately one-half of the starting and stopping housing IIiI. The casing I62 comprises the other half of the starting and stopping housing Hill. Within the casing I69 is disposed a through arcuate slot W3 particularly shown in Fig. 16. Also in the casing I66 and disposed over the slot I63 but not extending all the way through the casing I68, and extending somewhat beyond the ends thereof, is a slot I64. Secured in the main housing I and ext-ending therefrom in a direction parallel to the axis of the shaft I36, through the slot I553 of the casing I66 and into the slot IE4 is a pin I65. The outer end of the pin I65 is squared as at I66. Extending through the squared portion I66 is a pin I61 and projecting from each end of the slot I66 and into the same are pins I68 and I 69. Disposed within the slot 56% is a helical spring I'IO abutting at one end against the end of the slot I64 and at the other end against the squared end I66 of the pin I65. The spring I76 is maintained in position by the Similarly disposed on the opposite side of the squared end I66 and within the slot I96 is a second helical spring III. The effect of the slot I63 is to limit rotary movement of the casing I66. The effect of the springs I'Ill and III is to resiliently maintain the casing I60 in a predetermined position with respect to the pin I65. That is, should the casing I66 be rotated one way or the other, release of the rotating source will result in the springs I and I'll returning the casing I60 to its normal predetermined position.

Referring further to Fig. 16 a pin I I5 is secured in the casing I66 and extends upwardly into the slot H6 in the casing I62. Thus oscillatory movement of the casing I66 which is freely mounted on the shaft I36 will move the pin I in the slot IIIE. On striking either end of the slot I16 the pin will move the casing I62 therewith. Also, secured to the casing I60 is an arm I TI for manual oscillation thereof. The casing I62 is keyed to the shaft I36 so that oscillation of the casing I66 ultimately results in a corresponding oscillation of the shaft I36 which, as heretofore explained, results in axial movement of the main clutch rod 3 3 by the fork I37.

The operation of so much of the starting and stopping mechanism as has been described is as follows: Downward movement of the arm I56, as shown in Fig. 16, will bring the pin I'I5 into engagement with the upper end of slot I'I6 with the result that the casing I62 is moved in a clockwise direction and in turn moves the shaft I36 in a clockwise direction. Referring now to Fig. 1, the rotation of the shaft I38, as viewed therein, is counter-clockwise, and the eccentric pin I35 is moved to the right to move the rod 34 to the right. This movement engages the main clutch having faces 32 and 29 and ultimately initiates feeding of traversing movement of the tool oarrying and supporting spindle II depending on whether or not the traversing clutch shown particularly in Fig. 4 is in or out of engagement. On release of downward operating force against the arm I56 the springs I16 and I'll operate to return the casing I66 to normal position with respect to the pin I65.

Shown most clearly in Figs. 8 and 13 and in Figs. 14 and 16 is the mechanism for locking the casing I62, and consequently the main clutch having faces 32 and 29, in operating position. The operation of the machine as a whole is such that at the end of each complete cycle both feeding and traversing movements of the tool are stopped. This operation is initiated from a cam I86 on the surface of the sleeve I0. See Fig. 8. The cam I86 is so positioned that at the end of a cycle it will engage the axially movable pin I8I slidably mounted in the main housing I and the cover plate I82 of the traversing change speed gear box 12.

Extending through the casing I62 and part way into the casing I66 is a depression I83. Disposed over the depression I83 is a latch I84 having an adjustable head I35. The latch I84 is pivoted at I86 between its ends to the bracket I8'I extending from the cover plate I82 of the traversing change speed gear box i2. Pivoted at I 88 to the bracket I89, also .extending from the cover plate I82, is a lever I 96, its pivotal point being substantially midway between its ends. At one end IE3! it is pivoted to the pin I8I and at the other end I92, it is pivoted to the end of the latch I 84 away from its head I85. Disposed beneath the pivotal point I92 connecting the latch I82 and the lever I96 is a cylindrically shaped hollow member I95 closed at its outer end and open at its inner end, slidably mounted in the bore I86 and urged yieldably upward by the helical spring I91 bearing against the outer end of the member I95 and the bottom of the bore I96,

to maintain a yielding force against the pivotal point I92 to normally urge the latch I84 downwardly. Disposed at the lower end of the bore I95 is a vent I98 for permitting free movement of the member I95. Thus when the casing I62 moves in a clockwise direction as viewed in Fig. 16, the head I85 is yieldingly urged into the depression I83 when the lower edge I99 thereof passes it, thereby locking the casing I32 in its adjusted position. While the head I85 is out of the depression I83 and is urged against the outer face of the casing I62, it rides in an annular guiding groove 200.

Referring again to Figs. 8 and 13it will be evident that when the cam I80 comes in position beneath the pin I8I and cams it upwardly, the

lever IQI) will be pivoted about the point I88 and the latch I84 will be pivoted around the point I86 to raise the head I85 from its locked position in the depression I83. The helical spring 31, particularly shown in Figs. 1 and 3, will then be free to axially move the rod- 34 to open the main clutch having faces 32 and 29 to stop the rotation of the feeding and traversing cam I2.

In order to make possible the manual stopping of the feeding and traversing cam I2 at any desired time, the portion of the depression I83 within the casing I60, see Fig. 13, is provided with a sloping edge 22I. Secured to the latch I84 is a camming block 222. The camming block 232 is positioned on the latch I84 so that when the head I85 is within the depression I83, it is within the portion of the depression I83 disposed in the casing Hill. The latch I84 may then be lifted by camming up the block 202 by the edge 2M. This may be done by pressing the button operated valve I41. Compressed air is thus admitted to the cylinder I42 driving the piston I4I upwardly. This movement, through the arm I56, rotates the casing I60 in a counter-clockwise direction as viewed in Fig. 16. The sloping edge 2IlI of the depression I83 then cams against the sloping face 283 of the camming block 202 and raises the latch I84 together with its head I85 from the depression I83 with the result that the main clutch having faces 32 and 29 is disengaged as heretofore described. The manual stopping may be accomplished by the arm I'I'I instead of by the piston It I, if necessary or desired.

The structure for transforming the rotation of the cam I2 into feeding and traversing movement in the spindle II is particularly shown in Figs. 1, 15, 17 and 18. Concentrically disposed within the sleeve 'IEl supporting the feeding and traversing cam I2 is an axially slidable quill 2H3. The quill 2W is spaced from the sleeve III by liners 2i I. Secured to the quill or integrally formed therewith is an attachment head 2I2 to which a drilling and tapping head may be attached in a well known manner. Within the head 2I2 the spindle II is mounted for rotation in the bearing 2I3. The spindle II has in the head 2I2'an enlarged end 294 having a shoulder 2I5 bearing against the bearing H3. The head M2 is designed to receive a driver for actuating the drilling and tapping head (not shown) which is bolted to the attachment head 2I2 in .amanner well known. Disposed inwardly of the machine on the spindle II is a collar 2H3 having a set screw 2I'I which maintains the spindle II against axial movement with respect to the quill 2H3 so that axial movement of the quill is transferred to the spindle II. a

The head 2I2 is maintained against rotation and laterally moved by the rods 2 I8 slidably sup- 2I8 are secured by pinning or otherwise.

with grease.

ported inthe end plate 3. See Figs. and 17. The rods 2I8 are provided with shoulders 2I9, are threaded at their outer ends and are rigidly secured to the head 2I2 by the nuts 22B. Axial movement is imparted to the rods 2 I8 by the frame 22I which in turn receives movement in a direction parallel to the axes of the rods 2I3 by the feeding and traversing cam I2.

The frame 22I has two vertically extending arms 222 shown most clearly in Fig. 15. It is in these vertically extending arms that the rods The lower portion 223 of the frame 221 is centrally bored and is slidably mounted on a rod 224. The

rod 224 is supported at one end by the front cover plate 3 and secured thereto by set screws 225. The opposite end of therod 224 is disposed in a bore 226 in the central partition 2. Slidably mounted on the sleeve 22? extending around the rod 224 from the frame 22I is a block 228 yieldably held to the frame 22I. The yieldable connection between the frame 22I and the block 228 comprises elongated screws 229 slidably mounted in the lower portion 223 of the frame 22I and threaded into the block 228, and the helical springs 23% disposed between the lower portion of the frame 22I and the heads of the screws 229.

The lower portion 223 of the frame 22I is extended in a direction parallel to the axis of the rod 222 to provide between the lower portion 223 and the block 228 a channel 23I. Rotatably mounted on opposite sides of the channel 2 3I, one in the lower portion 223 and the other at the block 228, are rollers 232 and 233 for receiving therebetween the feeding and traversing cam I2. Thus, as the cam I2 is rotated the frame 22I carrying the rods M8 is moved back and forth in a direction parallel to. the axis of the tool supporting and driving spindle II. The springs 239 are strong enough to prevent back lash and jumping at the instant the cutting tool breaks through a surface or as friction upon the tool is released, preventing hogging of drills into the work and chipping of drill lips yet permitting relative yielding between the rollers 232 and 233 to take up any wear that may occur and assure smooth traversing and feeding action. It will be clear that the-curvature of the cam I2 at the points of intersection of the helical portions 12a and I2b, that is, the point at which the direction of movement of the follower is reversed, must correspond to the curvature of the rollers 22?. and 233 to accommodate the rollers 232 and 233.

Viewing the machine as a whole in Fig. 1 it is noted that the main housing I is divided into two chambers, A by the front cover plate 3 and central partition 2, and B by the central partition 2 and the rear cover plate 4. In operation the chamber B housing the gear mechanism of the machine is filled with oil and chamber A is filled In order to maintain within the chambers A and B the grease and. oil, respectively, all openings are fitted with the usual stufiing boxes and packing rings, or the like. It'will also be understood that the moving parts are suitably journaled and fitted with the usual bearings if necessary. These details, however, are'not part of the present invention and, therefore, are not described in full.

' The operation of the machine is as follows: Power is supplied to the machine through the pulley I driving the hollow shaft 6. The tool supporting spindle I I is splined within the hollow shaft 6 for axial movement and is constantly rotated thereby. The feeding and traversing mechanism is driven from the gear l5 on the hollow shaft 5 and is stopped at the end of each cycle of operation, namely, a complete revolution of the feeding and traversing cam l2, by the cam Hm engaging the pin IBI, to actuate the starting and stopping mechanism shown in detail in Fig. 16.

Power from the gear I5 is transferred to the main operating clutch having toothed faces 32 and 28 shown particularly in Fig. 3 by the gears l6 and 25. The gear it is driven from the gear 25 when the main clutch is engaged. Both the traversing and feeding drives are taken from the gear 49. The feeding drive comprises the gear 4! in mesh with the gear 50, the worm E3, the worm gear M and the shaft 55 to the change speed gear box shown in Fig. 7, and thence to the shaft 54 on which is mounted the overrunning clutch 59 shown in Fig. 5. The traversing drive is taken from the gear all by the gears 75 and I8 to the traversing clutch shown in Fig. 4, and the gears 9'5 and 9'! to the gear St in the change speed gear box l2 shown in Fig. 14. A connection is therein made by gears Hi0 and H to the shaft 6!, the latter also being connected to the overrunning clutch 59. The manner in which the overrunning clutch operates has been clearly described and therefore is not repeated. The spindle II is movedaxially with feeding or traversing speeds depending on the rate of rotation of the cam l2. Thus while the spindle l I is traversing the cam I2 rotates at a higher rate of speed than when it is feeding.

The machine according to this invention is changeable from drilling to tapping by making appropriate changes and adjustments which will be apparent to one skilled in the art.

Having thus described my invention what I claim and desire to secure by Letters Patent is:

1. A machine of the character described comprising a tool carrying spindle mounted for axial and rotative movement, means to rotate said spindle, and mechanism for providing said spindle with a slow feeding movement and a rapid traversing movement, said mechanism including a sleeve continuously rotatable in one direction through a complete cycle of operation surrounding said spindle, a cam extending around said sleeve and connected thereto, means controlling the movement of said cam, and yieldable means operatively connected to said spindle and operated by said cam.

2. A machine of the character described comprising a tool carrying spindle mounted for axial and rotative movement, means to rotate said spindle, and mechanism for providing said spindle with a slow feeding movement and a rapid traversing movement, said mechanism including a sleeve continuously rotatable in one direction through a complete cycle of operation surrounding said spindle a cam extending around said sleeve and connected thereto, means connected to said spindle and operated by said cam, an overrunning clutch, a feeding drive connected to said overrunning clutch, a traversing drive connected to said overrunning clutch, means for operating said cam from said traversing drive, and means for clutching said traversing drive into and out of operation whereby when said traversing drive is clutched out of operation the same is driven through said overrunning clutch at feeding speed and when said traversing drive is clutched into operation the same is rotated at rapid traversing speed.

3. A machine of the character described comprising driving means, a rotatable and axially movable tool carrying spindle splined therein, an axially movable quill concentrically disposed around said spindle and secured to said spindle for axially moving the same, a rotatable sleeve concentrically disposed around said quill, a feeding and traversing cam secured to and coaxial with said sleeve, means to rotate said sleeve at feeding and traversing speeds, and a connection between said cam and said quill for imparting to said quill, feeding and traversing axial movement, said cam being characterized by the fact that it is continuously rotatable in one direction through a complete cycle of operation and that the movement imparted by it to the quill is at a constant rate both stroke and return.

4. The invention as defined in claim 3 wherein the connection comprises yieldable means.

5. The invention as defined in claim 3 wherein the connection comprises a slidable frame including a yieldable follower.

6. In a machine of the character described, the combination of a rotatable and axially movable spindle, means to rotate said spindle and mechanism for axially moving said spindle, said mechanism including a rotatable double end cam, a follower for said cam, and means connecting said follower to said spindle, said follower comprising two yieldably engaged members spaced apart to form a channel for receiving said cam.

'7. In a machine of the character described, the combination of rotating means, a tool carrying spindle mounted for axial and rotative movement splined in said rotating means and mechanism for providing said spindle with feeding and traversing axial movement, said mechanism comprising a traversing shaft, an operative connection between said traversing shaft and said spindle for providing the same with feeding and traversing axial movement, an overrunning clutch connected to one end of said traversing shaft, driving means forming a driving connection between said overrunning clutch and said rotating means, traversing means forming a driving connection between said rotating means and said traversing shaft, a main clutch in said driving means and a traversing clutch in said traversing means whereby the main clutch in the driving means controls both the feeding and traversing, and the traversing clutch controls the traversing only.

8. In a machine of the character described, the

combination of a tool carrying spindle mounted for axial and rotative movement, means to rotate the spindle, means including a clutch to axially move said spindle at traversing speed, and mechanism for controlling said clutch, said mechanism comprising a rotatable drum, an axially slidable rod contiguous with the surface of said drum, a clutch operated by said rod, a dog secured to the surface of said drum for moving said rod in axial direction, means for positively locking said rod in axially adjusted position, and a second dog for releasing said locking means, whereby said traversing drive is clutched into and out of operation.

9. In a machine of the character described comprising a tool carrying spindle mounted for axial and rotative movement, means to rotate said spindle, and mechanism for providing said spindle with slow feeding movement and rapid traversing movement, said mechanism including a sleeve surrounding said spindle, a cam continuously rotatable in one direction throughout a complete cycle of operation having a constant pitch screw stroke portion extending around said sleeve and connected thereto,.means connected to said spindle and operated bylsaid cam,lan overrun ning clutch, afeeding drive connected to said overrunning clutch, a traversing drive connected to said overrunning clutch, means for operating said constant pitch cam portion from overrunning clutch at feeding speed and when said traversing drive is clutched into operation the same is rotated for rapid traversing speed.

10. In a machine of the character described the combination of a rotatable and axially movable spindle, means to rotate said spindle, and mechanism for axially moving said spindle, said mechanism including a rotatable unidirectional stroke and return double end cam continuously rotatable in one directionthroughout a complete cycle of operation having a constant pitch screw stroke portion, a follower for said cam, and means connecting said follower to said spindle, said follower comprising two relatively yieldable members spaced apart to form a channel for receiving said cam. i

11. In a machine of the character described, the combination of a rotatable and axially movable spindle, means to rotate said spindle and mechanism for axially moving said spindle, said mechanism including gear mechanism, a rotatable unidirectional stroke and return double end cam continuously rotatable in one' direction throughout a complete cycle of operation having a constant pitch screw stroke portion, a follower for saidcam, saidfollower comprising a frame, a block yieldably connectedto said frame and adjacentthereto, defining a channel with said frame for receiving said rotatable cam, means supporting said follower for movement parallel to the axis of said spindle, and means connecting said follower to said spindle said cam bearing against the frame side of said channel to move said spindle in a forward direction and against the block side of said channel to move said spindle in a return direction. i

12. In a machine of the character described,

i the combination of a rotatable and axially movable spindle, means to rotate said spindle and mechanism for axially moving said spindle, said mechanism including gear mechanism, a rotatable unidirectional stroke and return double end cam continuously rotatable in one direction throughout a complete cycle of operation having a constant pitch screw stroke portion, a follower for said cam, said follower comprising a frame dle in a forward direction and against the block side of said channel to move said spindle return direction.

13. A machine of the character described comprising a housing, a partition in said housing ina dividing the same into front and rear compartments, a front wall for said housing, a sleeve journaled in said rear compartment, a quill journaled in said front compartment, a, spindle splined to said sleeve and journaledin said quill, said quill and spindle projecting through said front wall, and mechanism for reciprocating said quill, said mechanism comprising means driven by said sleeve in said rear compartment, a cam in said front compartment driven by said means, a follower for said cam, and means projecting through said front wall connecting said follower to said quill outside of said front wall.

14. A machine of the character described comprising a housing, a partition in said housing dividing the same into front and rear compartments, a front wall for said housing, a sleeve journaled in said rear compartment, a quill journaled in said front compartment, a spindle splined to said sleeve and journaled in said quill, said quill and spindle projecting through said front wall, and mechanism for reciprocating said quill, said mechanism comprising means driven by said sleeve in said rear compartment, and a cam in said front compartment driven by said means, for reciprocating said quill.

15. A machine of the character described comprising a housing, a compartment in said housing having front and rear'walls, a sleeve journaled in said walls, a quill coaxial with said sleeve and slidably mounted therein, a spindle journaled within said quill and coaxial therewith, an endless cam mounted on said sleeve and coaxial therewith, a follower for said cam, a connection between said follower and saidquill to reciprocate said quill, and means to rotate said sleeve and spindle.

16. A drilling machine comprising a rotatable tool spindle, means for rotating said spindle, a

reciprocable carriage structure having a fixed forward and return stroke in which said spindle is supported for rotation and reciprocation to ward and from the work piece, a cam follower connected to said carriage for reciprocating the same, a cam to which said follower is geared for imparting both forward and return movement to said carriage, means for positively driving said cam in one direction. throughout a complete cycle of operation and during the complete forward and return movement of said carriage, said cam being continuous with a constant pitch screw portion for the forward stroke and a constant pitch screw portion for the return stroke, means for controlling and regulating the speed of rotation of said cam rotating means so as to selectively impart to said carriage both feeding and rapid traversing speeds while said follower is traversing one of said constant pitch screw portions of said cam whereby a multiplicity of various movements as to feed and rapid traversing may be imparted to said carriage without change in shape and construction of said cam.

17. A drilling machine comprising a rotatable tool spindle, means for rotating said spindle, a

reciprocable carriage structure having a fixed forward and return stroke in which said spindle is supported for rotation and reciprocation toward and from the work piece, a cam follower connected to said carriage for reciprocating the same, a cam to which said follower is geared for imparting both forward and return movement to said carriage, means for positively driving said cam in one direction throughout a complete cycle of operation and during the complete forward and return movement of said carriage,

said cam being continuous with a constant pitch screw portion for the forward stroke, means for controlling and regulating the speed of rotation of said cam rotating means so as to selectively impart to said carriage both feeding and rapid traversing speeds while said follower is traversing said constant pitch screw portion of said cam whereby a multiplicity of various movements as to feed and rapid traversing may be imparted to said carriage without change in shape and construction of said cam.

JQSEPH F. BUHR.

CERTIFICATE 0F CORRECTION. 7 Patent No'. 2,095,546. September 21,- 1957.

JOSEPH F. BU'HR. v

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Page 1+, first co1umn, line 58, for the word "arms" read arm; and s'ecohdcolumn, line 51 for "of" first occurrence read or g and that the said Letters Patent should be read with these corrections therein that the same may conform to the record of the case in the Patent Office. I Signed and sealed this 26th day of October, A. D. 1937.

Henry Vari Arsdale (Seal) I I Acting Commissioner of Patents. 

